Indexing mechanism for machine tools



E. P. BULLARD, 3D

Filed May 18, 19394 oct. 21, 1941,

E. P. BULLARD, 3D

INDEXING MECHANISMy FOR MACHINE TOOLS 5 Sheets-Shet 2 Filed May 18, '1939 f//l//fA K Al y 7J" 'K J J A lZ E l 27 L \26 z 1i K L' f 5 3f' 253e 3166 l .a3 u l 6? 63 5/71071 7J 8 7 7a l ,l I

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` INDEXING MECHANISM ROR MACHINE TooLs A' Filed May 18,4 1959 s sheets-sheet 3 IN1/Emma Enwam: I? BL/Lmna' vprovides a much greater time Patented Oct. 21,1941

iNDExlNG rmomuvrsM` Fon MACHINE e 'rooLs e l Edward P. Bullard, lll, Fairfield; Conn., assigner l.

to The Bullard Company, a corporation o! Connecticut Application May 18, 1939, Serial'No. 274,345

(onze-5o) 30 Claims.

This invention vreni-.es to machine tqlsof the type in which a work-supporting carrier is periodically indexed througha predetermined num.- ber of degrees about an axis to present a plurality of work-pieces to successive. stations where various yoperations are performed thereon, and particularly to. the mechanism employed for indexing the carrier.

While the principles of this invention may' applied to any machine tool in which a member.

is adapted to b'e periodically indexed, they will be described as applied to the-,type of machine tool disclosed in Patent 2,086,852 granted to E. P. Bullard et al. on. July 13, 1937.

Machine tools of the type disclosed in the above-referred-to patent usually include a standard about which va spindle-supporting carrier is adapted to be indexed. The spindles are positively drivenby inter-meshing gears at speeds which may be different for different spindles deo pending upon the operations to be performed on the work at successive stations about the machine.' When the carrier is tobe indexed, these intermeshing g'jears areA disengaged with the result that the speedof the spindles decreases, or may be different "from that of ay succeeding positive drive. Upon completion of =the indexing move'- ment and prior to re-establishing the positive' drive, an'impositive drive is employed to synchronize the-speed of the spindle gears with that of the constantly rotating `positive driving gears.

A commonindexing shaft is usually employed tov control the mechanism for synchronizing they speed of the spindle'gearswith that of the positive driving means, as well as .to positively driveq the carrier indexing mechanism. This common indexing shaft rotates througha single revolution during a complete indexing. movement of the carrier. Only a portion f its' revolution how-..`

ever, is necessary for indexing they carrier, and

- can perform.

necessary for the operation of the synchronizing 4 mechanism. Consequently, during each indexing movement considerable time is lost, thereby materially limiting the speed at which such machines Certain prior Iknown machines employ a crank member', for indexing 'the carrier, 'which' rotates- :at a constant speed. :The crank contacts means on the carrier and imparts a Genevaftype motion thereto subjecting the carrier to a substantially variable acceleration. The carrier must, of course, be accelerated and decelerated during its Vindexing movement. The manner in which this accelerationvaries directly affects the operation of the machine'tool since the force necessary to overcome the changing acceleration is the product of the mass of the carrier and its acceleration at a given instant.

The point of contact between the crank pin of the constant velocity single crank and the carrier initially approachesand iinally recedes from the center of the carrier, while at the same time the' tangential velocity imparted to the carrier in-` itially increases and finally decreases. Such a "condition produces substantially a maximum variation in the acceleration of the carrier during an indexing movement and consequently causes excessive stressing of the machine parts.

Machines of the above-described type require a' readily engageable and Ydisengageable positiveA drive between the common indexing shaft and its driving means. Accordingly, a positive-action clutch is commonly employed for this purpose in lwhich a mechanically-operated plunger xed tothe common indexing shaft is projected into a 4-slot..formed in therim of a constantly rotating v 'clutch element. The slots of such a clutchmust be of much greaterA length than the width of the only a portion of its revolution is required Ito y control the synchronizing mechanism.

Due to the mass of 'the carrier,- thespindles and the work that is supported '/'b'y'futhe spindles, the speed at which the carrier can be indexed is definitely limited. However, ithasfbeen found that 1 the speed of rotationor the common ,indexing shaft necessary to control the synchronizing-- mechanism may be much greater than thespeed l at which said shaft must be rotated to index the carrier Without overtaxing' theindexing mechanism. In otherwords, the speedof rotation of theicommon shaft to index the carrier 'properly interval than is 5s clutch prevents the plunger in order to enable-the plunger `(a xed element) to properly engage with the clutchelement (a rotating element). Since the spindlesupporting carrier is accelerated during theiirst half, and decelerated indexing movement, this prior-known type-of clutch has been taken up.' Consequently, the carriers travel is abruptly interrupted, causing it to `slam,`and excessively vstressing the parts of the kmachine, thereby detrimentally affecting its life y and operation. l

An object of this invention is to provide ama- 'chine tool of the above-described type capable of overcoming these and other dimculties.

during the last half of its .carrier -from beginning itsl deceleration until after the lost motion of the'A works F associated with each head.

chronized with that of a positive continuously operating driving means in a much shorter time interval than was heretofore possible; the pro- -vision of such a machine tool in which a common drive shaft is employed to control the spindle drive-changing mechanism, or the spindle synchronizing mechanismand for driving the carrier indexing mechanism; the provision .of such a machine tool in which the common indexing shaft is rotated fast enough to-eect a spindledrive change, or a synchronization of the spindle speed with that ora continuously operating driving means ink minimum time, and in which means is provided between the common indexing shaft and the indexing mechanism for decreasing the speed at which said shaft drives the indexing mechanism; the provision of such a machine tool in which the common indexing shaft may 'be readily connected to and disconnected from a rotating positive-action clutch element, which connection is effective in either direction and contains no back-lash; and the provision of such a machine tool in which the kinetic energy of the rotating spindle carrier may be effectively ab sorbed during'an indexing movement.

'Ihe above and other objects and novel `features of the -invention will become apparent from a consideration ofthe accompanying specification andthe attached drawings, in which,

' Figure l is a skeleton elevation view of a multiple spindle machine tool embodying the principles of this invention, certain elements having been omitted for clarity.

Fig. 2 is a sectional elevation view of part of the machine shown in Fig. l, disclosing the novel combination of' certain ofthe elements which form the present invention;

Fig. 3 is a sectional plan view taken substannauy along the une a-e of Fig. 2;

Figs. 4, 5 and 6 are diagrammatic views illustrating three positions of the compound or double crank employed to index the carrier about its central axis: g A

Fig. 7 is lan enlarged plan view taken substantially along line 1 1 of Fig. 1, showing the positive-action clutch mechanism; andl Fig. 8 is a sectional elevation view taken substantially along line 8 8 of Fig.

Referring to Figs. 1 and 2, the principles of this invention are shown as applied to a vertical multiple-spindle lathe comprising a base D that supports a vertically-disposed standard E upon which is mounted a plurality of tool heads H (only one of which is shown). 'I'he tool heads H are adapted to be yreciprocated vertically at various .speeds by motors M and M1,and a feed A spindle-supporting carrier C is journaled on the standard E and is adapted to support a plurality of work-supporting spindles J spaced about s its central axis'. The spindles J are adapted to be driven by a positive drive while a working op-` eration is being performed, and to be disengaged from said positive drive when the carrier C is to be moved about its central axis through an indexing movement.

The carrier C is indexed by a compound or double crank mechanism I, which `coacts with means on the carrier C to impart a modified Geneva type of movement to the carrier C and to move it through a predetermined number of 'degrees to position the spindles J under different tool-heads H. After the spindlesJ are disconnected from the positive drive, and during the indexing of the carrier C, their speed of rotation decreases, or may be different from that of the succeeding positive drive. Upon completion of the indexing movement of carrier C the spindles J must be re-connected to the continuously-rotating positive drive. Accordingly, a synchroniz.

K is adapted to be driven by the motor M and to s be connected to and disconnected therefrom by a feed works' control Fc and a positiveaction clutch P. One continuous revolution of the shaft K causes the positive drive for4 the spindles J to be disengaged; the carrier C to be unlocked by lowering a locking pin L; the carrier C to be indexed about itscentral axis by the indexing mechanism I; the locking pin L to be reengaged; the speed of rotation of the spindles J to be raised to that oi. the positive drive by the synchronizing mechanism S; and the positive drive to be re-engaged with the spindles J, all in the order named. y

Referring to Figs. l and 2the base D of the machine comprises a substantially cylindrical member I0, in the center of which is located an elevated lplatform Il that forms a support for thestandard E as well as a support for the driving mechanism for the spindles J.

The vertically disposed standard E comprises al substantially tubular shell I2, the lower end -mecha-nism for the spindles J may be located.

Referring to Fig. 1, the substantially tubular standard E is adapted to support the tool heads H (only one of which is shown) for vertical reciprocable movement.- The upper portion of standard E in the present instance is of octagonal cross-section thereby providing seven flat surfaces within which guideways I5 for seven separate tool heads `H maybe provided, and` an eighth flat surface on which no head is mounted, thereby rendering one of the spindles J free for a work-loading station.

The tool head I-Il comprises a body I6 into which an operating shaft I1 is threaded. The shaft I1 is adapted to be rotated inV either direction and at different speeds by the motors M 4and M1 and the feed Works F. It is to be understood that each head H is connected to the motors M and Ml through its own individual feedworks F. Inasmuch as the feed-works for each head H is identical, only one has been illustrated,

' posed vertically along and since the feed-works forms no Dart of the Referring'to Fig. 1, themotor Ml is a reversing motor adapted to rotate the shaft I1 in either direction at a relatively highspeed for bringing the tool head H rapidly down into feeding position and for rapidly retractlng said tool head after the machining operation on the workl has been completed. The motor M1 drives the shaft I1 through the gear train- I8 and through the.

clutch member |9 that is splined to the shaft Il; Motor M drives the shaft I1 in only one direction'- through they gear trains 2|, 22, 23, 24, 25, and the clutch |9. Movement of the clutch |9 upwardly causes a rapid traverse of the head lH in a. direction depending uponthat in which motor Ml is rotating; while movement of clutch I9 downwardly feeds a tool secured in head Hv intol vengagement with work that is supported by the spindles J on thecarrier C.

Referring to Fig. 2, the carrier.C comprises a substantially annular-shaped member 26 having a bearing-portion' 21 adapted to be journaled on the lower end of the standard E, and a thrustbearing portion 28 adapted to bear against an anti-friction thrust bearing-29 permanently secured to thelower end of' the standard E. The spindles J are journaled in the carrier C and located about its central axis. Referring to Figs.

1 and 2, the motor M feeds the head H during a cutting operation, and such feeding should bear a denite relation 'to the rate at which the spindles J aredriv'en. Accordingly, the motor M, through the gear trains 20 and 2|, drives shafts 30 (Fig. 2) which transmits the power from the motor to the spindles J. Shafts 30, one foreach spindle-J except the spindle located at the loading station, are disposed about the gear train 20 so that each may be rotated by the motor M. Their rotation is transmitted to the spindles J through identical gear trains including gears 3|, 32, 33, 34 and 35, the last of which is fixed to the respective spindles J. By selecting the proer gears in the train 2|, it is apparent that each of the shafts 30 as well 'as the spindles J may be driven at any pre-determined speed independently of every other.

Referring again Fig- 1, the operation, sete ting,`and control of the head H is automatically attained by the feed-works control Fe. This mechanism likewise forms no part of the present invention, vand its description -will also be limited to merely an'understanding of the present invention. A more specific description of the control Fc may be found in Patent #2,086,852, granted July 13, V1937, to E. P. Bullard, et al. The mechanism Fc may be set in advance to control the' operation of its respective head H. When the head'H has been retracted. from the work, following the completion'of a working operation, a disc 3B associated with the control Fe will assume a position where a plunger 31 will coact with a notch 38 inv thesurface of said disc. Such action-of the'plunger releases means to effect engagement of the shaft K with the motor M through the positive-action clutch P.

Referring to Figs. 1 and 2, the shaft K is disshaft-41 is, driven by the motor M throughfone gear of the train 20 and a 'gear 48 fixed to the end of. shaft 41 oppositethat which supports gear 46. Accordingly, clutch'element 42 continuously rotates so long as the motor M is energized.` As previously stated, the adapted to be rotated through a single revolution for each indexing movement of the carrier C, and therefore must Abe readily connected to and disconnected from the clutch element 42. Referring to Figs. '7 and 8, a bracket 49 is keyed to shaft K and its one arm 50 is bored to receive a radially-reciprocable plunger 5|. arm 52 of the bracket 49 receive another radially-reciprocable plunger for a purpose which will be described later. The arm 50 of bracket 49 also supports a pivot pin 53 on which a bell-crank 54 is pivoted. One arm of the bell crank 54 is connected to the plunger 5| by a pin 55 that extends through a cut out portion 56 of arm 50. The other arm of the bell-crank 54 is connected. to a drum 51 The drum 51 is journaled on the shaft K and is connected to the arm 50 of bracket 49 by a tension spring 60. The drum 51 is provided with lugs 6| spaced about its periphery, each of which is adapted to be engaged by one of the plungers 31 of the respective feed-works controly mechanisms Fc (Fig. 1).

During a working operation, the plungers 31 are adapted to engage the lugs 5| andto hold the drum 51 in a position turned clockwise from Y causes slot 59 tomove p in 58 and consequently to turn bell-crank 54 in a counterclockwise dig rection about its pin 53. This movement of" bellcrank 54 forces the plunger- 5| radially .outwardly into one of the slots 44 of the clutch element 42. Inasmuch as the plunger 5| is fixed to the non-rotating shaft K and is moved into engagement with the rotating. element 42, the slots 44 must be much longer than the width of the plunger 5| in order to provide ample .time for the plunger to get into driving position before a trailing wall 62 of a slot 44 engages it. Near the end ff a single revolutionof shaft K, means (not shown) causes the disc 36 (Fig. l) of 'the control Fc tostart rotating again so that the plunger 31 is forced into the path of they lugs 6I on the drum 51, thereby preventing continued rotation of said drum. As the shaft K and bracket 49 continue to rotate in a counterclockwise direction (Fig. 7), spring 60 is tensioned. 'Since pin 58 remains in a fixed position, being engaged-by the wallsy of slot 59 of drum 51, and pivot 53 moves with the bracket 49, the arm of the bell-crank 54 which is connected to the plunger 5| will move ina clockwise shaft K is The other A is likewise bored to.

the last of the heads plunger I from .the slot 44A in the Amotion to the carrier.

directionabout pivot 53 thereby withdrawing the clutch element 42.

Referring to Fig. 2, the gears 32 of the gear trains which form the positive drive for the spindles J are splined to shafts 63, so that said gears may be raised out of, or lowered into mesh with gears 33 while at all times remaining in mesh with gears 3|'. Movement of the gears 32 is controlled by the action of a cam 64 on shaft K which cam is adapted to raise a sleeve 65 that is slidably mounted on said shaft. The sleeve 65 supports vertically-movable rods 66 which are urged downwardly by springs 61 bearing against arms 68,-the latter being pinned to rods 66. v

The arms 68 engage extended hub portions of gears 32 so that vertically upward movement of sleeve 65 by the cam 64 causes the positive drive between shafts 30 and spindles J tobe disengaged. The cam 64 is positionedon the shaft K so that when the latter begins to turn during its single revolutionthe gears. 32 are immediately raisedout of mesh with gears 33.

When it is/desired to re-engage gears 32 with the gears 33, it is necessary to synchronize the speed of gears 33 with that of gears 32 in order to prevent gear clash. Accordingly, each gear 33 is provided with an integral skirt 69 which forms one element of a friction clutch. The other element 18 of the friction clutch is attached to one end of a synchronizing drive shaft 1I that is splined to and adapted to slide in a hubbed gear 12 (Fig. 2). The hubbed gear 12 is journaled vin the platform H of the base D, and is driven by a gear 13 keyed to the shaft 63. Therefore, by selecting gears of the proper size and raising shaft 1| far enough to effect engagegpe'nt between the clutch element 10 and-the skirt portion 69,*the speed of gears 33 may besynchronized with that of the gears 32.

Upward movement of the shafts 1I is controlled bythe rotation of shaft K through a cam 14 fixed thereto. The cam 14 is adapted to raise and lower a spider 15 journaled on the shaft K. 'Ihe outer ends of the arms ofthe spider 15 are resiliently connected to the lower ends of syn- Ychronizing drive shafts 1 I.

The cams 64 and 14 are positioned about shaft K so that upon its revolving through a single revolution, the positive drive for the spindles J is disengaged; then after a predetermined time interval, the speed of gears, 33 is` synchronized with that of gears 32 and 'the positive drive is re-established.

forming part of the mechanism I. The crank pin 16 is adapted to' contact inverted channelshaped .shoes 18/on the under surface of the carrier C to impart a modified"Geneva'type and 6, the crank pin `16 initially and, nally en- Referring to Figs. 4, 5

with that of the positive. drive so that the spindles may be lie-engaged with said drive. These two functions must be maintained in a definite timed relation and inasmuch as the shaft K is adapted to control both., the ratio between the rotation of shaft K and that of the crank pin 16 must be ,1:1, votherwise the timed relation of these two functions will vary during successive indexing operations. It vhas been found that if the shaft K is rotated rapidly enough to effect synchronization of the spindle speed with that of the positive drive in a minimum time, the shaft K will drive the crank pin 16 at too great a speed for proper and safe indexing of the carrier C. Accordingly, some means must be provided between the shaft K during at leasta portion of its revolution and still maintain between said shaft and said crank pin a 1':1 ratio of rotation.v The provision of the indexing mechanism` I between the shaft K and the crank Apin 16 accomplishes this result. By way of illustration, it isrepresented as a compound indexing -crank adapted to be rotated at a variable speed through a singlerevolution during an indexing movement. v Referring to Fig. 2, the indexing mechanism V`I comprises the crank arm 11fxed .to one end of a crank shaft 18 that.rotates about'anaxis Z. 'I'he opposite end of shaft 19 rigidly supports an arm 86 located 180 away from the crank arm 11. The under surface of arm 80 includes aV groove 8l which .forms a cross-head connection with a block 82 mounted on a gear 83, which y gear is adapted to be rotated at a constant velocity by shaft K and at a 1:1 ratio therewith through gears 84 and 85.

Referring again to Figs, 4, 5 and 6, it is apparent that the angular velocity of the crank arm 11, and in a like manner the tangential velocity of the crank pin 16, varies between a maximum at a point Xand a minimum at point Y (Fig. 4) depending upon the distance between the block 62 and the center Z about which the compound crank rotates,

' velocity of crank arm` 11 varies inversely as the of said pin. Therefore, the angular velocity j imparted to the' carrier C'by' the pin 16 is initially zero (Fig. 4) gradually increasing to a maximum (Fig. 5), and thence decreasing r.tozer' as the pin 16 leaves the s'hoe 18 (Fig.6). At a specific timed relation with the indexing of'carrier C,.the above-described mechanism S must synchronize 'the speed of the spindles J distance between block 82 and the axis Z. As stated before, only a portion of the revolution of crank pin Y16 is required to index the carrier C through an indexing movement. Therefore, by .selecting the. low-velocity portion of the travel of crank pin 16 for indexing the carrier C, the rotation of shaft K, which drives the crank pin 16, may be substantially increased and still drive the carrier within a safe' speed. Furthermore, the aboveA selection enables the mechanism Sy to be operated during the highvelocity portion oi' the `travelof crank pin 16 and rtherefore within a minimum time interval. Additionally the above constructionpovides a 1:1 ratio of rotation between the shaft K and the crank pin 16. 'Ihis variable-speed indexing mechanism I produces a smoother indexing action thancan be obtained with the'constant speed single crank of the prior art and therefore causes less straining of the machine. There are two conditions inherent in the us`e of the single crank which have a detrimental effect upon the indexing action of the carrier, namely, (1) the point of contact between the' `crank pin and the "carrier approaches and recedes from the center of the carrier, and (2)' the velocityy imparted to th'e carrierv increases 4and decreases respectively 'I'nat is, the angular v '2,259,948 lcarrier were .of infinite length, it is clearthat the movement of the carrier bythe constant velocity single crankV would be one of simple harmonic motion. However, since the radiusof the carrier is not-of infinite length, the two' conditions enumerated have an additive effect which materially disturbs the motion 'imparted to the carrier. The first ofthe above conditions is also inherent' in the double crank indexing mechanism'I of this invention.' However, by

selecting that portion of the movement of crank pin 16 on each side of its minimum velocity position Y (Fig. 4), to index the carrier C..it is reciprocated into and out of' engagement with alug 88 on the carrier C by a cam 86 iix'ed to the arm 80 of the indexing mechanism I. Inasmuch as the cam 86 rotates with the crank shaft 19, its setting may be arranged to time the release of the carrier C with the indexing movement of the crank pin 16 to maintain a proper sequenceof operation between the locking pin L and the indexing of the carrier C.

The shaft K, which drives thecrank-pin 16,

must accelerate the carrier C during the iirst halfpand decelerate said carrier during the last half of an indexing movement. Since the 'shaft K is driven by the otor M through the positive clutch P, and the clutch includes slots 44 that are much longer than the width of the plunger 5|,

means must be provided to eliminate the back lash between the slots 44 and plunger 5I.

Referring again to Figs. 7 and 8, the arm 52 of the bracket 49 is bored to receive a radially re. lciprocable plunger 89 that is resilien-tlyurged outwardly by a compression-spring 90'. The

plunger 89 is provided with a head portion hav- 1 ing an inclined surface 9| that is adapted to engage 'the leading end ofthe slots 44. A camming pin 92 is xed in the head of drum 51 and extends downwardly through an elongated 'slot 94 which coact to retract the plunger 89 from within slot 44 upon relative movement in'one direction between the drum ,51 and the bracket 49.

In the position shown in Figs. 7 and 8, the element 42 is driving the shaft -K through 'the drum 51, the bracket 49, and the plungers 5i and 89. The connection has no lost motion or back lash and consequently acceleration and decelerationofl the carrier C will be instantly'accomplished. Upon moving-a plunger 31 into .the path of lugs ever, the bracket 49 continues to rotate in a counter clockwise ldirectionl causing the plunger 89 to move relatively tothe pin 92 an'd camming the plunger 89 from withinslot 44. Upon subsequently releasing drum 51, and by virtue of the.

slot 93 1in arm 52, the contraction of spring 69 eiects relative movement between the drum 51 and the bracket 49, causing sliding ofthe camming surfaces 94 andpermitting the spring 90y to movelthe plunger 499 outwardly.

DuringV the indexing of carrier C. its velocity is increased to amaximum during the rst half of the indexing movement. The kinetic enersyof Vthe carrier due tok thismaximum'velocity is .sub-

stantial, especiallyfwhen heavy work is mounted on the spindles J. rIhe .absorption of this kinetic energy by the indexing mechanism I and shaft K places an unreasonable strain on the machine causing distortion of parts andslammirig of the carrier with'the locking pin L. In the "present invention. meanshas been providedior braking the movement of the carrier only after it has at- 'tained its maximum velocity, and only until the indexing movement of the carrier has been s ubstantially-completed. Referring to Figs. 2 and 3. a portion of the arm 89 ofthe indexing mechanism I forms a'braking surface 95 about which a brake band 96 is positioned'. One end of the brake band 96 is connected to the sidewall of the base D, and the other end is connected by a pin 91 to a lever 98 pivoted to the sidewall of the base D. rThe free end ofthe pivoted lever 98 is provided with. a cam follower 99 adapted to follow a cam -inllnxedon'the crank shaft 19. The

. cam `lill) is positioned on the crank shaft 19 so that it moves lever 99 to render the brake band 96 effective only after the carrier C has attained its maximum velocity. The brake band 96 is released upon completion of the indexing move- I ment.

v erable independently of the operation of said 93 in arm 52 which yslot overlies the bore in-which plunger 89 reciprocates. The plunger 89 and' pin 92 are provided with cooperating"camv surfaces' 6| on the drum 51, the drum is stopped. Howf` Although the various `features of the improved machine tool have been shown and described in vdetail to fully disclose one embodiment of this invention, it will be evident that numerous changes may be made in such details, and certain features may be used without others, without departing irom'the principles of the invention.

What is claimed is:

1. A machine tool comprising in combination a work-supporting carrier; means for feeding a tool support relative to said carrier; means for successively indexing said carrier about its central axls'including a member` adapted to be rotated at a variable speedthrough a single revolution during each indexing movement; lmeans optool support feeding means 'for rotating said member; and means on said carrier adapted to be engagedA by said -member ior indexing saidfcarrier during the slow speed portion of the variable speed cycleof said member.

2. A machine tool as claimed "in claim 1, in which said member is' driven at a variable speed through each revolution-and said member contacts meanson said carrier atvarylng distances from the central axis of said carrier.

3. A machine tool comprising in combination,

a work-supporting carrier; means for feeding a tool support relative to said carrier; means for successively indexing said carrier about its central axis including a member adaptedvto be rotated at a variable speed during a. single revolution foreach indexing movement: means operable independently of the operation of saidtool support feeding means for rotating said member; and means on said carrier adapted to be contacted by said member,v for a relatively short time interval before and after said member reaches its minimum speed.

'4. A machine `tool as claimed in claim 3, in which said member contacts the means on said carrier successively at decreasing distances from center of said carrier.

of contact approaches the center of said carrier, y

and increases as said point recedes from the 6. A machine tool as claimed in claim 3, in which said member is operated by a driving member adapted to be rotated at substantially a constant speed.

7. A machine tool comprising in combinationi a base; a standard; a carrier journaled on said standard and adapted to be periodically indexed about said standard; a plurality of work-supporting spindles mounted on said carrier; means for positively Adriving said spindles; means for indexing said carrier; means for changing the drive between the spindles and said positive drive; means for operating said drive changing means at a speed to change said drive 4within substantially a minimum time interval; and means for operating said indexing means in a definite timed relation with that of the change drive mechanism, but at a relatively slower speed.

8. A machine tool as claimed in claim 7, in which said indexing means includes a rotatable crank pin, and said change-drive means is operated by rotatable cam means; a common shaft adapted to be rotated at substantially a constant speed for rotating said cam means and said crank pin in a definite timed relation during each revolution of said shaft; and means between said shaft and said crank pin for rotating said crank pin at `a slower rate of speed during at least a portion of the rotation of said shaft than the speed at which saidv cam means is rotated.

9. A machine tool comprisingin combination, a carrier; a plurality of work-supporting spindles mounted on said carrier and disposed about its central axis; means for driving said spindles; means for disengaging said driving means from and for engaging .said driving means with said spindles; means for indexing said carrier about its central axis while said driving means is disengaged from said spindles including a member Aadapted to be rotated at a variable speed through a single revolution during each index, ing movement.

' indexing means during at least a portion of adapted to be rotated ata variable speed through l0. A machine tool comprising. in combination,

a carrier; a pluralityof work-supporting spindles mounted von said carrier and disposed about its central axis; means for driving said spindles; means for disengaging said spindles from and for engaging said spindles' with said driving means; means for periodically indexing said carrier about its central axis including' a member adapted to be rotated at a variablespeed through a single revolution during each indexing movement; and common meansfor controlling the disengagement and engagement of the spindles with the driving means and for operating said indexing means. l

11. A machine tool as claimed in claim 10 in which said common means includes a shaft adapted to be rotated through a single, revolution during each indexing movement, and in which said shaft is rotated at a speed sufficient to disengage said spindles from and to engage said spindles with said driving means within substantially a minimum time interval; and means between saidv shaft and said indexing means for decreasing the speed at which said shaft drives said indexing means.

12. A 'machine tool comprising in combination, a carrier; a plurality of work-supporting spindles mounted on said carrier and disposed about its central axis; means for positively driving said spindles; means for disengaging said positive driving means from, and for engaging said'positive driving means with said spindles; means for indexing said carrier about its central axis while said positive driving means is disengaged from said spindles including a member adapted to be rotated at a variable speed through a single revolution during each indexing movement;l and means for synchronizing the speed of said spindles with that of said positive driving means prior to re-engagement of said positive driving means with said spindles.

13. A machine toolas claimed in claim 12, in which -the indexing of said carrier occurs during the low-velocity portion, and the synchronizing of said spindles occurs during the high velocity portion of the cycle of revolution of said member.

14. A machine tool comprising, in combination, a standard; a carrier surrounding said standard and provided with a plurality of work-supporting spindles spaced about the central axis of said carrier; means for driving said spindles; means for engaging and disengaglng a positive and an impositive drive between said spindles and said spindle driving means, whereby the speed of said spindles may `be synchronized with the speed of said positive drive before said positive drive is engaged with said spindles; means for indexing said carrier about said standard after disengaging saidpositive and before engaging said impositive drive with said spindles; a common shaft for controlling the synchronizing of the speed of said spindles with that of said positive drive and for driving said indexing means; means for driving said common shaft at a speed to eifect said synchronizing within substantially a minimum time interval; and means between said common shaft and said indexing means for decreasing the speed at which said common shaft drives said the revolution of said common shaft.

15. A machine tool as claimed in claim 9, in which said indexing means comprises a member a single revolution during each Aindexing movement, and in which said member contacts means on said carrier for moving it through an indexin movement.

16. Av machine A which said indexing means comprises a member adapted to be rotated at a variablespeed vthrough a single revolution during each indexing movement and in which said member contacts means on said carrier at varying distances from its central axis.

17. A machine tool as claimed in claim 9, in`

which said indexing means comprises a member adapted to be rotated from a maximum through a minimum to a maximum speed through a single revolution during each indexing movement; and in which said membercontacts means on said .carrier for a relatively short time interval beforey and after said member reaches its minimum tool as claimed in claim 9, in'

' arm of variable effective length.

cra'nk comprises an additional crank having an 19. A machine tool as-claimed in claim 9, in

' which the indexing means comprises a crank,

and the means between said common shaft and said lcrank comprises an additional crank, said additional crank being adapted to form a crosshead connection with a member adapted to be means adapted to brake said carrierpnly after said carrier has attainedits maximum velocity,

and only until said carrier has substantially returned to rest.

21. Av machine tool as claimed in claim 20, in which said indexing means comprises a member adapted to be rotated at a variable speed through mally stationary indexing shaft adapted periodically to be rotated through a singlerevolution when said carrier is'to be indexed; a positiveaction clutch element journaled on said indexing shaft and having a plurality of slots disposed about its periphery; means adapted .to drive said clutch element at substantially'. a constant rotative speed; a mechanically-operated reciprocable plunger connected to said normallystationary indexing shaft and adapted to be moved into .and withdrawn from engagement with walls' of the slots in said clutch element, said slots width of said plunger; and means between said indexing shaftand said positive clutch for eliminating the back-lash betweensaid plunger and the relatively long slots.

23. A machine tool as claimed in claim 22, in

` which`the back-lash eliminating means comprises a resiliently urged plunger connected to said indexing shaft and adapted to engage the walls of said slots opposite those which said mechanically-operated plunger engages.

24. A machine tool as claimed in claim 22, in

which said indexing means is adapted tomovev said carrier throughout its indexing movement; and'brake means adapted to be applied to said .ically driving said -ber adapted to be rotated at a variable speed through a single `revolution during each indexing movement; a common-shaft adapted to be rotated through 4a single revolution for controlling the synchronizing of the speed of said spindles with that of said positive drive and for driving said indexing means; means for periodcommon shaft for a single revolution at a speed to eifect said synchronizing within substantially a minimum time interval, said means comprising a positive-action clutch; means between said commonr said shaft drives said indexing means during'at least a portion of the revolution of said shaft; and meansadapted to brake said carrier only after said -carrier has attained a maximum velocity during an indexing movement, and only until said carrier has substantially returned to a single revolution during each indexing move- `being substantially greater in length than the indexing means only after said carrier has att 25. A machine tool comprising, in combinaion, of tool heads about its central longitudinal axis; a carrier encircling said standard; a plurality of work-supporting spindles mounted on said carrier and spaced about its central axis; means'for driving said spindles; means forvengaging and disenga'ging a positive and an impositive drive between said spindles and said spindle driving means, 'whereby the speed of said spindles may be synchronized withthe speed ofsaid positive drive before said positive drive is engaged with said spindles; means for periodicallyy indexing said carrier through a predetermined numberlof degrees about its central axis comprising a memtained its maximum velocity. and only until said v carrier has returned substantially to rest.

a standard adapted to support a plurality rest.

26. Indexing apparatus for machine tools comprising an indexingmember adapted periodically to be moved about a closed path; means for moving said indexing through each of its cycles, said means comprising a driving member mounted on one shaft, a driven member mounted on a separate'spaced shaft, and a cross-head connection between said driving and driven members.

27. Indexing apparatus for machine tools comprisingl a 'crank pin adapted to be moved about a closed path; means connecting said pin to a rotatable shaft; and means for driving said shaft at a variable speed throughout each-of its revolutions comprising 4a. rotatable member mounted on a separate spaced shaft, and a cross-head connection between said rotatable member and said rotatable shaft.

28. Indexing apparatus for machine tools comprising a crank pin adapted'to be moved about a` closed path; means for driving said pin at a variable speed throughout said path, said vdriving means comprising a pair of crank arms mounted on one shaft, one of said arms forming a crosshead connection with a rotatable member mounted on a separate spaced shaft and adapted to be rotated-at a substantially constant speed.

29. In a machine tool, a shaft adapted to be rotated periodically; cooperating positive-action clutch elements mounted on said shaft; one of said elements being journaled on and the other being xed to said shaft; means for rotating the element that is `iournaled on said shaft; one of said elements being -provided with a plunger, and the other including a plurality of circumferentially disposed slots of greater length than the width of said plunger; means for periodically plunger into one of said slots; and

back lash between saidinserting said means for eliminating the slot and plunger.

30. In a machine tool, a haft adapted to be rotated periodically; a positive-action clutch elementjournaled on said shaft; means for'rovtating said element; a cooperating clutch element fixed to said shaft;

shaft and said indexing means for decreasing the speed at which member at a variable speed of circumferentially disposed slots of` 

